U.S. patent number 9,828,938 [Application Number 15/163,405] was granted by the patent office on 2017-11-28 for piston for internal combustion engines.
This patent grant is currently assigned to NATIONAL UNIVERSITY CORPORATION SHIZUOKA UNIVERSITY, SUZUKI MOTOR CORPORATION. The grantee listed for this patent is National University Corporation Shizuoka University, SUZUKI MOTOR CORPORATION. Invention is credited to Kunio Hayakawa, Naoyuki Suda.
United States Patent |
9,828,938 |
Suda , et al. |
November 28, 2017 |
Piston for internal combustion engines
Abstract
A resin coat film 39 formed on a skirt portion 10 of a piston 7
has a four-sided outer peripheral region knurled at upper and lower
regions thereof corresponding in a rear view of the piston 7 to an
upper skirt part 36 and a lower skirt part 38 of the skirt portion
10 extending in parallel with an axial direction of left and right
piston pin boss portions 15 and 14, with a combination of short
vertical grooves 43A and 43B and medium-length vertical grooves 42A
and 42B extending in parallel with a central axis C of a piston
crow portion 9, and at left and right edge regions thereof, with
long vertical grooves 41.
Inventors: |
Suda; Naoyuki (Shizuoka,
JP), Hayakawa; Kunio (Shizuoka, JP) |
Applicant: |
Name |
City |
State |
Country |
Type |
SUZUKI MOTOR CORPORATION
National University Corporation Shizuoka University |
Shizuoka
Shizuoka |
N/A
N/A |
JP
JP |
|
|
Assignee: |
SUZUKI MOTOR CORPORATION
(Shizuoka, JP)
NATIONAL UNIVERSITY CORPORATION SHIZUOKA UNIVERSITY
(Shizuoka, JP)
|
Family
ID: |
57281882 |
Appl.
No.: |
15/163,405 |
Filed: |
May 24, 2016 |
Prior Publication Data
|
|
|
|
Document
Identifier |
Publication Date |
|
US 20160348611 A1 |
Dec 1, 2016 |
|
Foreign Application Priority Data
|
|
|
|
|
May 25, 2015 [JP] |
|
|
2015-105538 |
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F02F
3/022 (20130101); F02F 3/10 (20130101); F02F
3/28 (20130101); F05C 2225/00 (20130101) |
Current International
Class: |
F02F
3/10 (20060101); F02F 3/02 (20060101); F02F
3/28 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
Primary Examiner: Amick; Jacob
Attorney, Agent or Firm: Rothwell, Figg, Ernst &
Manbeck, P.C.
Claims
The invention claimed is:
1. A piston for internal combustion engines comprising: a piston
body; a pair of skirt portions hanging down from the piston body; a
pair of piston pin boss portions hanging down from the piston body
and configured to hold a piston pin; a pair of side wall portions
configured to interconnect the pair of skirt portions and the pair
of piston pin boss portions; and a resin coat film provided on an
outer periphery of one skirt portion of the pair of skirt portions,
the one skirt portion comprising: a central skirt part having an
outside diameter thereof maximized at a central part thereof with
respect to an extending direction of a central axis of the piston
body; an upper skirt part residing above an upper boundary of the
central skirt part, and curved to have an outside diameter thereof
gradually decreased, as the upper skirt part extends from the upper
boundary toward the central axis of the piston body; and a lower
skirt part residing below a lower boundary of the central skirt
part, and curved to have an outside diameter thereof gradually
decreased, as the lower skirt part extends from the lower boundary
toward the central axis of the piston body, the one skirt portion
being configured to have increased curvatures, as the one skirt
portion circumferentially extends from a circumferential central
region on the one skirt portion toward the pair of side wall
portions, the resin coat film comprising a region thereon
corresponding to a combination involving at least the upper skirt
part and the lower skirt part, the region on the resin coat film
being knurled with a set of vertical grooves extending in parallel
with the central axis of the piston body, the set of vertical
grooves residing within an outer peripheral range of the resin coat
film corresponding to extending directions of the pair of piston
pin boss portions with respect to a direction perpendicular to the
central axis of the piston body.
2. The piston for internal combustion engines according to claim 1,
wherein the set of vertical grooves comprises a first subset
thereof involving first and second vertical grooves mutually
neighboring in a circumferential direction of the one skirt
portion, the first vertical groove being nearer to the
circumferential central region of the one skirt portion and shorter
in the extending direction of the central axis of the piston body,
than the second vertical groove.
3. The piston for internal combustion engines according to claim 2,
wherein the set of vertical grooves has the first subset thereof
residing in a first outer peripheral region of the resin coat film
corresponding to the upper skirt part of the one skirt portion.
4. The piston for internal combustion engines according to claim 3,
wherein the set of vertical grooves comprises a second subset
thereof involving third and fourth vertical grooves mutually
neighboring in the circumferential direction of the one skirt
portion, the third vertical groove being nearer to the
circumferential central region of the one skirt portion and shorter
in the extending direction of the central axis of the piston body,
than the fourth vertical groove, wherein the set of vertical
grooves has the second subset thereof residing in a second outer
peripheral region of the resin coat film corresponding to the lower
skirt part of the one skirt portion.
5. The piston for internal combustion engines according to claim 1,
wherein the set of vertical grooves comprises vertical grooves
having depths thereof within a range of 5 .mu.m to 20 .mu.m.
Description
CROSS-REFERENCE TO RELATED APPLICATION
This application is based upon and claims the benefit of priority
from Japanese Patent Application No. 2015-105538, filed May 25,
2015, the entire contents of which are incorporated herein by
reference.
BACKGROUND OF INVENTION
Technical Field
This invention relates to pistons for internal combustion engines,
and specifically, to pistons for internal combustion engines
including skirt portions adapted to slide relative to a wall of a
cylinder bore.
Background Techniques
As a piston adapted to reciprocate relative to a wall of a cylinder
bore in an internal combustion engine, there has been known one
disclosed in JP 4,749,398. This piston includes a skirt body having
a pair of skirt portions hanging down therefrom, a pair of side
wall portions interconnecting the paired skirt portions with each
other, and a pair of piston pin boss portions provided at the
paired side wall portions for holding a piston pin.
The skirt portions are formed in a barrel shape including a
piston-axially central part having a largest outside diameter in
consideration of effects of thermal expansion. The skirt portions
each have a resin coat film formed thereon.
Further, the skirt portions each have an outer periphery including
left and right peripheral regions thrust-directionally covered with
lateral stripe-shaped films allowing for favorable lubrication,
thereby preventing the piston from seizing at such locations on a
cylinder.
SUMMARY OF INVENTION
Such the piston for internal combustion engines in the past is
provided, at both circumferential sides of each skirt portion, with
side wall portions connected to the piston pin boss portions
serving to support a piston pin that transmits combustion pressures
to a connecting rod.
By doing so, both sides of the skirt portions connected to side
wall portions have decreased tendencies to deform, accompanied by
increased contact pressures (in terms of a pressure per unit area)
acting on the skirt portions to press against the wall of the
cylinder bore. On the other hand, lower parts of the skirt portions
involving low rigidities and tendencies to elastically deform have
moderated low contact pressures.
Therefore, when the piston reciprocates, each skirt portion has
parts of such combustion pressures imposed thereon from the piston
pin. In due course, the skirt portion contact the wall of the
cylinder bore, when the skirt portion has a surface thereof
involving those regions undergoing high contact pressures and those
regions undergoing low contact pressures.
In addition thereto, the skirt portions formed in a barrel shape
have small clearances between the cylinder bore and local regions
having a largest diameter in piston-axially central parts, and
large clearances between the cylinder bore and piston-axially upper
and lower parts relative to the central parts.
In this regard, there may be situations involving arrays of pits
formed with an even depth at locations undergoing large contact
pressures and locations undergoing small contact pressures, on a
resin coat film at each skirt portion. Such arrays of pits are
effective to introduce oil to pits, and adapted for oil to flow out
of pits, acting on oil films, making the thickness thinner, thus
causing the skirt portion to contact the wall of the cylinder bore
with increased contact pressures. Hence, when running at low
speeds, there can be anxieties about insufficient oil supply
causing non-conforming lubrication at local parts of the skirt
portion undergoing small clearances to the wall of the cylinder
bore.
On the other hand, there can be local parts of the skirt portion
contacting the wall of the cylinder bore with decreased contact
pressures, undergoing increased clearances to the wall of the
cylinder bore, with anxieties about excessive oil supply. In such
situations, the piston is to reciprocate on the wall of the
cylinder bore, in manners of scraping oil at the piston-axially
upper and lower parts relative to the central part of the
piston.
As a result, there can be fluxes of oil constituting resistances,
causing piston shearing resistances, that is, piston dragging
resistances to be increased, with anxieties about degraded fuel
economy.
This invention has been devised in view of such problems.
It therefore is an object of this invention to provide a piston for
internal combustion engines adapted for favorable lubrication
between the piston and a wall of a cylinder bore, allowing for
reduced piston dragging resistances by oil.
According to aspects of this invention, there is provided a piston
for internal combustion engines including a piston body, a pair of
skirt portions hanging down from the piston body, a pair of piston
pin boss portions hanging down from the piston body and configured
to hold a piston pin, a pair of side wall portions configured to
interconnect the pair of skirt portions and the pair of piston pin
boss portions, and a resin coat film provided on an outer periphery
of one skirt portion of the pair of skirt portions. The one skirt
portion includes a central skirt part having an outside diameter
thereof maximized at a central part thereof with respect to an
extending direction of a central axis of the piston body, an upper
skirt part residing above an upper boundary of the central skirt
part, and curved to have an outside diameter thereof gradually
decreased, as the upper skirt part extends from the upper boundary
toward the central axis of the piston body, and a lower skirt part
residing below a lower boundary of the central skirt part, and
curved to have an outside diameter thereof gradually decreased, as
the lower skirt part extends from the lower boundary toward the
central axis of the piston body. The one skirt portion is
configured to have increased curvatures, as the one skirt portion
circumferentially extends from a circumferential central region on
the one skirt portion toward the pair of side wall portions. The
resin coat film includes a region thereon corresponding to a
combination involving at least the upper skirt part and the lower
skirt part, the region on the resin coat film being knurled with a
set of vertical grooves extending in parallel with the central axis
of the piston body. The set of vertical grooves resides within an
outer peripheral range of the resin coat film corresponding to
extending directions of the pair of piston pin boss portions with
respect to a direction perpendicular to the central axis of the
piston body.
According to the aspects of this invention, there can be achieved
adaptation for enhanced lubrication between a piston and a wall of
a cylinder bore, allowing for reduced piston dragging resistances
by oil.
BRIEF DESCRIPTION OF DRAWINGS
FIG. 1 is a cross-sectional right side view of an internal
combustion engine, as a figure showing a piston for internal
combustion engines according to an embodiment of this
invention.
FIG. 2 is a right side view of a piston fit in a cylinder bore of
the internal combustion engine, as a figure showing a piston for
internal combustion engines according to the embodiment of this
invention.
FIG. 3 is a rear view of the piston viewed from the side of a
driver's seat in an involved vehicle, as a figure showing a piston
for internal combustion engines according to the embodiment of this
invention.
FIG. 4 is a right side view of the piston, as a figure showing a
piston for internal combustion engines according to the embodiment
of this invention.
FIG. 5 is a bottom view of the piston fit in the cylinder bore, as
a figure showing a piston for internal combustion engines according
to the embodiment of this invention.
FIG. 6 is a longitudinal sectional view along a IV-IV arrowed cut
plane in FIG. 3 (i.e., viewed from the right side) of the piston
fit in the cylinder bore, as a figure showing a piston for internal
combustion engines according to the embodiment of this
invention.
FIG. 7 is a distribution pattern diagram illustrating a set of
positional relations between a rear side of the piston and contact
pressures to be exerted on a skirt portion of the piston, as a
figure showing a piston for internal combustion engines according
to the embodiment of this invention.
FIG. 8 is a diagram illustrating a set of positional relations
between a rear side of the piston and curvatures along a curved
outer peripheral surface of the skirt portion in an axial direction
of the piston (i.e., variations of curvature in the vertical
direction), as a figure showing a piston for internal combustion
engines according to the embodiment of this invention.
FIG. 9 is a distribution pattern diagram commonly illustrating a
set of positional relations between a rear side of the piston and
clearances that each of front and rear skirt portions of the piston
has to a wall of the cylinder bore, as a figure showing a piston
for internal combustion engines according to the embodiment of this
invention.
FIG. 10 is a distribution pattern diagram commonly illustrating,
for each of front and rear skirt portions of the piston, two
different sets of positional relations between a curved outer
peripheral surface thereof and vertical grooves formed in a resin
coat film layer thereon, as a figure showing a piston for internal
combustion engines according to the embodiment of this
invention.
FIG. 11 is a diagram commonly illustrating a distribution pattern
of clearances that each of front and rear skirt portions of the
piston has to the wall of the cylinder bore, as it is overlapped on
a distribution pattern of vertical grooves formed in a resin coat
film layer of that skirt portion, as a figure showing a piston for
internal combustion engines according to the embodiment of this
invention.
FIG. 12 is a diagram illustrating streams of oil on the piston in
an ascending state, as they are overlapped on the distribution
patterns in FIG. 11, as a figure showing a piston for internal
combustion engines according to the embodiment of this
invention.
FIG. 13 is a diagram illustrating streams of oil on the piston in a
descending state, as they are overlapped on the distribution
patterns in FIG. 11, as a figure showing a piston for internal
combustion engines according to the embodiment of this
invention.
FIG. 14 is a graph comparing a piston having vertical grooves
formed therein according to an embodiment of this invention and a
piston in the past having no vertical grooves, with respect to a
piston performance defined by a relationship between an engine
revolution speed and a frictional force produced between a wall of
a cylinder bore and skirt portions of a piston.
DESCRIPTION OF EMBODIMENTS
There will be described pistons for internal combustion engines
according to embodiments of this invention, with reference to the
drawings.
The drawings include FIGS. 1 to 14 as figures describing a piston
for internal combustion engines according to an embodiment of this
invention.
It is noted that FIGS. 1 to 9 and FIGS. 11 to 13 each carries a
combination of arrowed frontward, rearward, rightward, and/or
upward senses indicating corresponding senses of
vehicle-longitudinal, vehicle-transverse, and vehicle-vertical
directions identified in a field of vision at a driver's seat in an
associated vehicle.
Description is now made of configuration of an internal combustion
engine involved in this embodiment.
FIG. 1 illustrates an engine 1 as the involved internal combustion
engine mounted on the associated vehicle. The engine 1 is made up
including a cylinder block 3 having a crankcase 2 integrated
therewith, and a cylinder head 4 provided at an upper portion of
the cylinder block 3.
The cylinder block 3 includes a set of cylinder bores 6 arrayed
vehicle-transversely (i.e., overlapped when viewed
vehicle-transversely), having one-to-one corresponding pistons 7
individually accommodated therein, respectively. The pistons 7 are
made of an aluminum alloy or the like. The pistons 7 are each
adapted to vertically reciprocate relative to an associated
cylinder bore 6.
The pistons 7 are respectively connected by one-to-one
corresponding connecting rods 8 to a common crankshaft 5, for
adaptation to convert reciprocal motions of the pistons 7 into
rotary motions of the crankshaft 5 through the connecting rods
8.
Here, at the engine 1, the cylinder bores 6 are provided in
correspondence to the cylinder number of the engine 1. For
instance, when assuming the engine 1 to be a 4-cylinder engine, the
engine 1 has four cylinder bores 6.
In the example illustrated in FIG. 1, the engine 1 is made up as a
4-cylinder engine. However, according to embodiments herein, the
engine 1 may well have an arbitrary specific cylinder number
without restriction to 4. Moreover, the engine 1 may well be made
up as another type of engine, such as a gasoline engine, or a
diesel engine. Further, the type of the engine 1 is not restricted
thereto.
The engine 1, being a 4-cylinder engine, includes four cylinder
bores 6 that have an identical configuration, and four pistons 7
that have an identical configuration, the pistons 7 being fit in
the cylinder bores 6, respectively. Depicted in FIG. 1 is a
combination of a specific cylinder bore 6 and a specific piston 7
fit therein. Description will be made the specific piston 7 fit in
the specific cylinder bore 6.
The piston 7 fit in the cylinder bore 6 has a lateral side shown in
FIG. 2, as it is viewed from the right side, and a longitudinal
section shown in FIG. 6, as it is viewed from the right side. The
piston 7 has a rear side shown in FIG. 3, a right side shown in
FIG. 4, and a bottom side shown in FIG. 5.
As will be seen from FIGS. 2 to 6, the piston 7 has a piston crown
portion 9 adapted to vertically reciprocate relative to a whole
circumference of a wall 6a being an inner peripheral wall of the
cylinder bore 6, and a pair of front and rear skirt portions 11 and
10 hanging down from the piston crown portion 9. Here, according to
embodiments herein, the piston crown portion 9 constitutes a piston
body according to this invention.
The piston 7 has a pair of left and right piston pin boss portions
15 and 14 hanging down from the piston crown portion 9, for
cooperatively holding a vehicle-transversely extending piston pin
16 (see FIG. 1) to be rotatable about a central axis C1 thereof
(see FIGS. 3 and 5).
Further, the piston 7 has a combination of a left pair of front and
rear side wall portions 13 and 13 (see FIG. 6) and a right pair of
front and rear side wall portions 12 and 12 (see FIG. 2), disposed
for interconnecting the front and rear skirt portions 11 and 10 and
the left and right piston pin boss portions 15 and 14.
Specifically, the piston 7 has four side walls 13, 13 and 12, 12
(see FIG. 5) being: a left front side wall portion 13 for
interconnecting a left side part 11a of the front skirt portion 11,
a front edge part of the left piston pin boss portion 15, and an
associated part of a lower bottom part of the piston crown portion
9; a left rear side wall portion 13 for interconnecting a left side
part 10a of the rear skirt portion 10, a rear edge part of the left
piston pin boss portion 15, and an associated part of the lower
bottom part of the piston crown portion 9; a right front side wall
portion 12 for interconnecting a right side part 11b of the front
skirt portion 11, a front edge part of the right piston pin boss
portion 14, and an associated part of the lower bottom part of the
piston crown portion 9; and a right rear side wall portion 12 for
interconnecting a right side part 10b of the rear skirt portion 10,
a rear edge part of the right piston pin boss portion 14, and an
associated part of the lower bottom part of the piston crown
portion 9.
As will be seen from FIG. 1, the piston pin 16 is formed in a
cylindrical shape, and as shown in FIG. 3 or 5, the central axis C1
of the piston pin 16 extends in a perpendicular direction to a
central axis C of the piston crown portion 9 and intake and exhaust
directions.
Here, as shown in FIG. 5, according to embodiments herein, the left
side parts 11a and 10a of the front and rear skirt portions 11 and
10 each correspond to one side in a circumferential direction of a
skirt portion according to this invention, and the right side parts
11b and 10b of the front and rear skirt portions 11 and 10 each
correspond to another side (i.e., an opposite side to the one side)
in the circumferential direction of the skirt portion according to
this invention.
It is noted that, as will be seen from FIGS. 2 to 6, the left side
parts 11a and 10a as well as the right side parts 11b and 10b each
have a prescribed circumferential length or width from a
corresponding one of left ends or right ends of the front and rear
skirt portions 11 and 10, respectively.
As shown in FIG. 2, 5, or 6, the left and right piston pin boss
portions 15 and 14 respectively have left and right piston pin
application holes 15A and 14A for the piston pin 16 to be fit
therein. The piston pin 16 is inserted through the left and right
piston pin application holes 15A and 14A, and supported by the left
and right piston pin boss portions 15 and 14.
As will be seen from FIG. 1, at the piston 7, the piston pin 16 is
operatively connected to a small-diameter portion 8A of an
associated connecting rod 8, and a large-diameter portion 8B of the
connecting rod 8 is operatively connected to the crankshaft 5. By
doing so, reciprocal motions of the piston 7 are converted into
rotary motions of the crankshaft 5.
As will be seen from FIG. 1, at the engine 1, the cylinder head 4
has a set of intake ports 21 formed therein for individual fluid
communication with the cylinder bores 6. Each cylinder bore 6 has a
combustion chamber 18 defined between a top region of a wall 6a
thereof and an associated piston 7. There can be fluxes of intake
air introduced to the combustion chamber 18, through an associated
intake port 12.
At the engine 1, the cylinder head 4 has a set of exhaust ports 22
formed therein for individual fluid communication with the cylinder
bores 6. At each cylinder bore 6, there can be fluxes of exhaust
gas produced in the combustion chamber 18 and discharged therefrom
through an associated exhaust port 22.
As will be seen from FIG. 1, at the engine 1, the cylinder head 4
is provided with a combination of an intake camshaft 23 carrying a
set of intake cams 23A, and an exhaust camshaft 24 carrying a set
of exhaust cams 24A. Further, at the cylinder head 4, each cylinder
bore 6 is provided with a combination of an intake valve 25
operable by an associated intake cam 23A to make or break fluid
communication with the combustion chamber 18, and an exhaust valve
26 operable by an associated exhaust cam 23A to make or break fluid
communication with the combustion chamber 18.
As shown in FIGS. 2 to 4 and 6, at the before-mentioned specific
piston 7, the piston crown portion 9 has at an outer periphery
thereof three ring grooves formed therein to be a first compression
ring groove 31, a second compression ring groove 32, and an oil
ring groove 33 in this order from the top.
At the above-noted piston 7, the first compression ring groove 31
and the second compression ring groove 32 have non-depicted annular
first and second compression rings fit therein, respectively, and
the oil ring groove 33 has a non-depicted annular oil ring fit
therein as a piston ring.
The first compression ring groove 31 as well as the second
compression ring groove 32 has a function of contacting a region on
a wall 6a of the cylinder bore 6, to thereby seal tight the
combustion chamber 18.
The oil ring has a function of contacting a region of the wall 6a
of the cylinder bore 6, moving in accordance with a reciprocal
movement of the piston 7, while scraping oil adhering on the region
on the wall 6a of the cylinder bore 6.
Further, as shown in FIG. 2, 3, or 4, the oil ring groove 33 has a
pair of front and rear sets of oil return holes 34 formed in a
(radially inward) bottom thereof. Specifically, there is one set of
oil return holes 34 (four locations, see FIG. 3) formed at each of
a thrust side and a counter thrust side (i.e., one and the other of
side thrust directions before and after a top dead center,
specifically, the front and rear sides in FIG. 2) of the piston
crown portion 9, thus two sets (four.times.2=eight locations) in
total. The oil return holes 34 each have open ends at the bottom of
the oil ring groove 33a and an inner peripheral region of the
piston crown portion 9, for fluid communication in between.
Here, the term `thrust side` means one side portion of the piston 7
to be forced in a stroke descending in the cylinder bore 6 from the
top dead center, to have forces due to rotating torque of the
crankshaft 5, acting in a thrust direction perpendicular to an
axial direction of the crankshaft 5, on an associated one-side
region of the wall 6a of the cylinder bore 6.
Further, the term `counter thrust side` means an opposite side
portion of the piston 7 to be forced in a stroke ascending in the
cylinder bore 6 toward the top dead center, to have forces due to
rotating torque of the crankshaft 5, acting in a thrust direction
opposite to the above thrust direction, on an associated
opposite-side region of the wall 6a of the cylinder bore 6.
As will be seen from FIG. 1, each cylinder bore 6 has a spatial
region defined by and between the wall 6a and an associated piston
7, where oil is supplied from an oil jet hole 8a provided through a
large diameter portion 8B of an associated connecting rod 8. By
doing so, as illustrated in FIG. 2 or 6, the cylinder bore 6 has a
film 35 of oil formed over a whole circumference of the wall 6a for
outer peripheral regions of the piston 7 (specifically, the piston
crown portion 9) to be brought into contact thereon.
Such supply of oil serves for cooling the piston 7, as well as for
lubrication between outer peripheral regions of the piston 7 and
the wall 6a of the cylinder bore 6. It is noted that there may well
be elements else than oil jet holes 8a, employed for such oil
introduction.
The engine 1 includes a non-depicted oil pan provided at a lower
portion of the crankcase 2, the oil pan communicating with each
cylinder bore 6. As an associated piston 7 vertically reciprocates
in the cylinder bore 6, the oil ring fit in the oil ring groove 33
of the piston 7 scrapes oil adhering on the wall 6a of the cylinder
bore 6. There can be fluxes of scraped oil conducted through oil
return holes 34 at the bottom of the oil ring groove 33, and
discharged onto inner peripheral regions at the piston crown
portion 9 of the piston 7, to return to the oil pan through spatial
regions between the front and rear skirt portions 11 and 10 of the
piston 7.
As will be seen from FIGS. 2 and 6, at the afore-mentioned specific
piston 7, the front and rear skirt portions 11 and 10 are adapted,
when the piston 7 reciprocates, to come into contact at the thrust
side or the counter thrust side with an associated region on the
wall 6a the cylinder bore 6, thereby exhibiting a function of
suppressing swing motions of the piston 7.
As illustrated in FIG. 3, at the above-noted piston 7, the rear
skirt portion 10 is formed substantially in a rectangular shape
(specifically, a rectangular oblong shape) in a rear view of the
piston 7, having a combination of two narrow sides extending in
parallel with the central axis C of the piston crown portion 9 and
two long sides extending in parallel with a perpendicular direction
(e.g., an extending direction of the axis C1 of the piston pin 16)
to the central axis C of the piston crown portion 9.
Also the front skirt portion 11 of the piston 7 is formed
substantially in a rectangular shape (specifically, a rectangular
oblong shape) in a front view of the piston 7, having a combination
of two narrow sides and two long sides, like the rear skirt portion
10.
As shown in FIG. 6 or 8, at the piston 7, the front and rear skirt
portions 11 and 10 have front and rear central skirt parts 37 and
37 as their central parts with respect to an extending direction of
the central axis C (i.e., an axial direction) of the piston crown
portion 9. The central skirt parts 37 and 37 constitute a maximal
outside diameter portion (as a combination of maximal radius parts)
of the front and rear skirt portions 11 and 10. In a side view of
the piston 7, as shown at the right half of FIG. 8 or 10, each
central skirt part 37 has an outer circumferential surface thereof
(arcuate in a plan view) constituting a circumferential surface of
a straight cylindrical shape having an axis in parallel with the
central axis C of the piston crown portion 9. Here, the central
axis C of the piston crown portion 9 overlaps a line of symmetry of
the front and rear skirt portions 11 and 10 (that is, they reside
on an identical straight line.)
Further, at the piston 7, the front and rear skirt portions 11 and
10 have upper skirt parts 36 and 36 thereof residing at upper
levels than an upper boundary (specifically, an imaginary upper
boundary plane) 37a of the central skirt parts 37 and 37,
respectively. As shown at the right half of FIG. 8, those upper
skirt parts 36 and 36 each have an outer peripheral surface thereof
formed, in the side view of the piston 7, in the shape of a half
arc segment of an inverted bowl. In the side view of the piston 7,
this bowl shape is curved with an outside diameter or radius
gradually decreased from a maximal outside diameter or maximum
radius (which is equal to an outside diameter or radius at the
upper boundary 37a of an associated central skirt part 37), toward
the central axis C of the piston crown portion 9, as it extends
upward from the upper boundary 37a.
It is noted that, in the side view of the piston 7, the upper
boundary 37a of the central skirt parts 37 and 37 is located at a
lower level than the central axis C1 of the piston pin 16 with
respect to an extending direction of the central axis C (i.e., in
an axial direction) of the piston crown portion 9.
Further, at the piston 7, the front and rear skirt portions 11 and
10 have lower skirt parts 38 and 38 thereof residing at lower
levels than a lower boundary (specifically, an imaginary lower
boundary plane) 37b of the central skirt parts 37 and 37,
respectively. As shown at the right half of FIG. 8, those lower
skirt parts 38 and 38 each have an outer peripheral surface thereof
formed, in the side view of the piston 7, in the shape of a half
arc segment of a normally put bowl. In the side view of the piston
7, this bowl shape is curved with an outside diameter or radius
gradually decreased from a maximal outside diameter or maximum
radius (which is equal to an outside diameter or radius at the
upper boundary 37a of an associated central skirt part 37), toward
the central axis C of the piston crown portion 9, as it extends
downward from the lower boundary 37b.
As will be seen from above, the graph at the right side of FIG. 8
(as well as a graph at the right side of FIG. 10) shows a profile
(specifically, a right side view) of a barrel shape (specifically,
a rear one of front and rear divided barrel shapes mutually
line-symmetrical with respect to the central axis C of the piston
crown portion 9) defined by a combination of six skirt parts being:
the upper skirt parts 36 and 36: the central skirt parts 37 and 37;
and the lower skirt parts 38 and 38.
In this graph, the horizontal axis represents a decrease in
diameter of the barrel shape (specifically, each of the upper and
lower skirt parts 36, 36 and 38, 38) relative to an associated
central skirt part 37, and the vertical axis represents a vertical
distance from a lower bottom of the barrel shape (specifically,
from a lower end of an associated one of the front and rear skirt
portions 11 and 10).
Such being the case, at the piston 7, the front and rear skirt
portions 11 and 10 constitute a barrel shaped portion.
It is noted that, in FIG. 6, the front and rear skirt portions 11
and 10 of the piston 7 are depicted to be significantly curved for
the convenience of description, while actually they are not so
significantly curved.
As shown in FIG. 5 being a bottom view of the piston 7, the front
and rear skirt portions 11 and 10 have gradually increased
curvatures at their upper skirt parts 36 and 36, central skirt
parts 37 and 37, and lower skirt parts 38 and 38, as the front and
rear skirt portions 11 and 10 extend from circumferential central
regions 11c and 10c thereon, in both circumferential directions
(i.e., as they approach the left and right side parts 11a and 11b
of the front skirt portion 11 or the left and right side parts 10a
and 10b of the rear skirt portion 10 that are connected to the
front left and front right side wall portions 13 and 12 or the rear
left and rear right side wall portions 13 and 12, respectively).
Accordingly, as shown in FIG. 5, the front and rear skirt portions
11 and 10 have curved outer peripheral surfaces thereof gradually
spaced apart from the wall 6a of the cylinder bore 6, with
gradually increased clearances in between.
At the front and rear skirt portions 11 and 10, the circumferential
central regions 11c and 10c constitute apexes on circumferences
(e.g., narrow local regions each extending along a radially most
bulged outside-line of a profile of the barrel shape in FIG. 8) of
the front and rear skirt portions 11 and 10 interconnecting front
or rear end part of the left side wall portion 13 and front or rear
end part of the right side wall portion 12 with each other,
respectively. Accordingly, on the barrel shape being a combination
of the front and rear skirt portions 11 and 10, its outer periphery
has a smallest clearance at the circumferential central regions 11c
and 10c relative to the wall 6a of the cylinder bore 6, as it
extends in a circumferential direction.
As will be seen from FIGS. 2 to 5, the front and rear skirt
portions 11 and 10 have front and rear resin coat films 39 and 39
formed over surface regions (excluding outside edges) of outer
peripheries thereof, with a prescribed thickness, by using a screen
method, for example. Those resin coat films 39 and 39 have low
friction resistances and high heat resistances.
The front and rear resin coat films 39 and 39 circumferentially
extend with respect to the barrel shape, covering respective outer
peripheries of the upper skirt parts 36 and 36, the central skirt
parts 37 and 37, and the lower skirt parts 38 and 38 of the front
and rear skirt portions 11 and 10 opposing the wall 6a of the
cylinder bore 6.
For instance, as shown in the left half of FIG. 8, the rear resin
coat film 39 (as well as the front resin coat film 39) has an upper
end 39a as an upper edge thereof extending alongside an upper edge
of the rear skirt portion 10, and a lower end 39b as a lower edge
thereof extending alongside a lower edge of the rear skirt portion
10.
Further, as shown in the left half of FIG. 8, the rear resin coat
film 39 (as well as the front resin coat film 39) has a left end as
a left edge thereof extending alongside a left edge of the left
side part 10a of the rear skirt portion 10, and a right end as a
right edge thereof extending alongside a right edge of the right
side part 10b of the rear skirt portion 10.
As shown in FIG. 2, 3, 4, 7, or 8 (in particular, as best shown in
FIG. 7), the rear resin coat film 39 (as well as the front resin
coat film 39) is knurled at an outer peripheral surface thereof
with a left set of five vertical grooves including: a left long
vertical groove 41 nearest to the left edge of the rear resin coat
film 39 (hence, nearest to the left edge of the rear skirt portion
10); an upper pair of short left vertical grooves 42A and 43A
neighboring an upper part of the left long vertical groove 41 in a
circumferential direction of the rear resin coat film 39 (hence, in
a circumferential direction of the rear skirt portion 10); and a
lower pair of short left vertical grooves 42B and 43B neighboring a
lower part of the left long vertical groove 41 in a circumferential
direction of the rear resin coat film 39.
Further, the rear resin coat film 39 (as well as the front resin
coat film 39) is knurled at the outer peripheral surface thereof
with a right set of five vertical grooves including: a right long
vertical groove 41 nearest to the right edge of the rear resin coat
film 39 (hence, nearest to the right edge of the rear skirt portion
10); an upper pair of short right vertical grooves 42A and 43A
neighboring an upper part of the right long vertical groove 41 in a
circumferential direction of the rear resin coat film 39 (hence, in
a circumferential direction of the rear skirt portion 10); and a
lower pair of short right vertical grooves 42B and 43B neighboring
a lower part of the right long vertical groove 41 in a
circumferential direction of the rear resin coat film 39.
The left five vertical grooves 41, 42A, 42B, 43A and 43B and the
right five vertical grooves 41, 42A, 42B, 43A and 43B are each
oriented to extend in parallel with the central axis C of the
piston crown portion 9, and are located within ranges in which the
left or right piston pin boss portion 15 or 14 extends, with
respect to (vehicle-transverse) directions perpendicular to the
central axis C of the piston crown portion 9 in a rear view of the
piston 7 (e.g., in the upper half of FIG. 7).
In other words, the left and right sets of vertical grooves 41,
42A, 42B, 43A and 43B are disposed within left and right
circumferential surface regions of the resin coat film 39 that
vertically overlap the left or right piston pin boss portion 15 or
14 (defined in part by broken lines) in FIG. 7.
As will be seen from FIGS. 3 to 5 and FIG. 7, at the rear resin
coat film 39 (or the front resin coat film 39, vice versa), the
left and right sets of vertical grooves 41, 42A, 42B, 43A and 43B
involve: `a combination of left upper and lower vertical grooves
43A and 43B and right upper and lower vertical grooves 43A and 43B
nearest to the circumferential central region 10c (or 11c) of the
rear skirt portion 10 (or the front skirt portion 11)`, as a
combination of shortest ones; and `a combination of left and right
vertical grooves 41 and 41 nearest to the left or right side wall
portion 13 or 12 at the rear side (or the front side) of the piston
7`, as a combination of longest ones.
Further, at the rear resin coat film 39 (or the front resin coat
film 39), the left and right sets of vertical grooves each involve
a combination of upper and lower intermediate vertical grooves 42A
and 42B interposed between an associated outermost vertical groove
41 and an associated combination of innermost upper and lower
vertical grooves 43A and 43B, the intermediate vertical grooves 42A
and 42B having a length thereof shorter than the outermost vertical
groove 41, and longer than each of the innermost vertical grooves
43A and 43B.
As shown in FIG. 7, at the rear resin coat film 39 (or the front
resin coat film 39), those upper and lower vertical grooves 42A and
42B, and 43A and 43B which are paired at the left side, and those
upper and lower vertical grooves 42A and 42B, and 43A and 43B which
are paired at the right side are formed in those upper and lower
regions on the outer peripheral surface of the resin coat film 39
which correspond to, that is, overlap the upper skirt part 36 and
the lower skirt part 38 of the rear skirt portion 10 (or the front
skirt portion 11) in a rear view of the piston 7, respectively.
Therefore, the paired upper and lower vertical grooves 42A and 42B,
and 43A and 43B are not formed any in that region on the outer
peripheral surface of the resin coat film 39, which corresponds to
the central skirt part 37 of the rear skirt portion 10 (or the
front skirt portion 11).
It is noted that there is no vertical groove formed in `a central
zone` of the outer peripheral surface of the resin coat film 39
that vertically extends at both sides of, and inclusive of, the
circumferential central region 10c (or 11c) of the rear skirt
portion 10 (or the front skirt portion 11), between the left pair
of upper and lower innermost vertical grooves 43A and 43B and the
right pair of upper and lower innermost vertical grooves 43A and
43B, which overlap axially inner ends of the left and right piston
pin boss portions 15 and 14, respectively, in the rear view of the
piston 7.
As shown in the left half of FIG. 8 being a rear view of the piston
7, at the rear resin coat film 39 (or the front resin coat film
39), the left upper vertical grooves 42A and 43A as well as the
right upper vertical grooves 42A and 43A are disposed to extend
vertically in the figure (i.e., in parallel with the central axis C
of the piston crown portion 9), in a region on the upper skirt part
36 of the rear skirt portion 10 (or the front skirt portion 11),
specifically between the upper end 39a of the resin coat film 39
and the upper boundary 37a of the central skirt part 37 of the rear
skirt portion 10 (or the front skirt portion 11), more
specifically, between the upper end 39a of the resin coat film 39
and the central axis C1 of the piston pin 16 (see FIG. 1).
Further, as shown in the left half of FIG. 8, at the rear resin
coat film 39 (or the front resin coat film 39), the left lower
vertical grooves 42A and 43A as well as the right lower vertical
grooves 42A and 43A are disposed to extend vertically in the
figure, in a region on the lower skirt part 38 of the rear skirt
portion 10 (or the front skirt portion 11), specifically between
the lower end 39b of the resin coat film 39 and the lower boundary
37b of the central skirt part 37 of the rear skirt portion 10 (or
the front skirt portion 11).
Further, in the left half of FIG. 8, the upper left and right
vertical grooves 42A and 42A of an intermediate length have lower
ends thereof in contact with the upper boundary 37a of the central
skirt part 37, and the lower left and right vertical grooves 42B
and 42B of an intermediate length have upper ends thereof in
contact with the lower boundary 37b of the central skirt part 37.
On the other hand, the upper left and right vertical grooves 43A
and 43A of a shortest length have lower ends thereof spaced upward
from the upper boundary 37a of the central skirt part 37, and the
lower left and right vertical grooves 43B and 43B of a shortest
length have upper ends thereof spaced downward from the lower
boundary 37b of the central skirt part 37. And, the left and right
vertical grooves of a greatest length are disposed to extend
vertically in the figure, over a range involving the upper skirt
part 36, the central skirt part 37, and the lower skirt part 38 of
the rear skirt portion 10 (or the front skirt portion 11).
FIG. 9 commonly shows, in an expanded map in the lower half, a
distribution pattern of clearances that the rear skirt portion 10
and the front skirt portion 11 have at their outer peripheries to
the wall 6a of the cylinder bore 6. It is noted that the map in
FIG. 9 is prepared as an overlapping rear view of the front and
rear skirt portions 11 and 10 from the driver's seat. In this map,
the front skirt portion 11 has left and right edges thereof mapped
as end parts 11L and 11R overlapping left and right edges mapped as
end parts 10L and 10R of the rear skirt portion 10,
respectively.
As shown in FIG. 9, at the rear skirt portion 10 (or the front
skirt portion 11), the outer periphery is formed in a four-sided
shape in a rear view of the piston 7, defined by the upper and
lower edges of the skirt portion 10 (or 11) as long sides, and the
left and right edges 10L and 10R (or 11L and 11R) of the skirt
portion 10 (or 11) as narrow sides.
The rear skirt portion 10 (or the front skirt portion 11)
constituting the barrel shape has most increased clearances to the
wall 6a of the cylinder bore 6 in regions at four corners being
upper and lower left and right corners of the four-sided outer
periphery, and most decreased clearances to the wall 6a of the
cylinder bore 6 in a transversely and vertically central region of
the outer periphery. In the map of FIG. 9, the hatching denotes
smaller clearances, as it has shorter intervals.
At the rear skirt portion 10 (or the front skirt portion 11), the
outer periphery has, at intermediate regions between the central
region and the regions at the four corners, such intermediate
clearances to the wall 6a of the cylinder bore 6 that are smaller
than at the regions at the four corners, and larger than at the
central region.
In the map of FIG. 9, the outer periphery of the rear skirt portion
10 (or the front skirt portion 11) includes a large clearance
region 51 defined by a connected region of the regions at the four
corners, a small clearance region 52 defined by the central region,
and an intermediate clearance region 53 defined by a connected
region of the intermediate regions, that is, a region between the
large clearance region 51 and the small clearance region 52.
In a rear view of the piston 7 shown in the upper half of FIG. 9,
the small clearance region 52 shown in the map in the lower half of
FIG. 9 resides in a vicinity of a point of intersection between the
central axis C of the piston crown portion 9 and the central axis C
of the piston pin 16. The small clearance region 52 has a
vertically elongate small elliptical shape.
In the rear view of the piston 7, the intermediate clearance region
53 has a seven-sided shape vehicle-transversely line-symmetrical
with respect to the central axis C of the piston crown portion 9.
The seven-sided shape includes: a top side vehicle-transversely
extending alongside the upper edge 39a (see FIG. 8) of the rear
resin coat film 39 (or the front resin coat film 39); a left
vertical side vehicle-vertically extending in parallel with the
left edge 10L (or 11L) of the rear skirt portion 10 (or the front
skirt portion 11); a right vertical side vehicle-vertically
extending in parallel with the right edge 10R (or 11R) of the rear
skirt portion 10 (or the front skirt portion 11); a left upper
oblique side interconnecting a left end of the top side and an
upper end of the left vertical side; a right upper oblique side
interconnecting a right end of the top side and an upper end of the
right vertical side; a bottom apex located in a vicinity of a point
of intersection between the central axis C of the piston crown
portion 9 and the lower edge 39b (see FIG. 8) of the rear resin
coat film 39 (or the front resin coat film 39); a left lower
oblique side interconnecting the bottom apex and a lower end of the
left vertical side; and a right lower oblique side interconnecting
the bottom apex and a lower end of the right vertical side.
The large clearance region 51 is defined by an entire region in the
four-sided shape on the outer periphery of the rear resin coat film
39 (or the front resin coat film 39), as a combination of the small
clearance region 52 and the intermediate clearance region 53 is cut
out, and involves upper and lower combinations of left and right
sub-regions corresponding to the regions at the four corners, the
sub-regions having substantially tri-angular shapes.
As shown in FIG. 11, according to embodiments herein, the rear
resin coat film 39 (or the front resin coat film 39) has the left
and right sets of five vertical grooves 41, 42A, 42B, 43A, and 43B
knurled in a region on the outer periphery of the resin coat film
39 corresponding to (i.e., overlapping in a rear view of the piston
7) the large clearance region 51 of the rear skirt portion 10 (or
the front skirt portion 11).
FIG. 10 shows, at a leftmost diagram therein, positional relations
between the right set of five vertical grooves 41, 42A, 42B, 43A,
and 43B and a right half region of the large clearance region
defined by the seven-sided intermediate clearance region 53 (see
FIG. 9) of the rear skirt portion 10 (or the front skirt portion
11), in comparison with a combination of a rightmost diagram
therein (identical to the profile at the right half of FIG. 8)
illustrating variations in curvature of along the outer periphery
of the rear skirt portion 10 (or the front skirt portion 11), and a
central diagram therein illustrating an example including a large
clearance region 51 defined by a circular arcuate boundary, while
connecting those diagrams by extending the upper and lower
boundaries 37a and 37b (see FIG. 8) of the skirt part 37 at the
rear skirt portion 10 (or the front skirt portion 11).
As will be seen from FIG. 10, among the set of five vertical
grooves at each of the left and right sides, the shortest upper and
lower vertical grooves 43A and 43B are knurled at those local
regions in vicinities of central parts at the oblique sides of the
seven-sided shape in the large clearance region 51 of the rear
skirt portion 10 (or the front skirt portion 11), which correspond
to outer peripheral regions of the upper and lower skirt parts 36
and 28 spaced circumferentially leftward or rightward off from the
circumferential central region 10c (or 11c, see FIG. 5) of the
skirt portion 10 (or 11), subject to clearances to the wall 6a of
the cylinder bore 6 to be minimized when the piston 7 operates.
As will be seen from FIG. 10, among the set of five vertical
grooves at each of the left and right sides, the longest vertical
groove 41 is knurled at that local region alongside the left or
right narrow side of the four-sided large clearance region 51 of
the rear skirt portion 10 (or the front skirt portion 11), which
corresponds to an outer peripheral region of the skirt portion 10
(or 11) residing nearest to the left or right side wall portion 13
or 12, subject to clearances to the wall 6a of the cylinder bore 6
to be maximized when the piston 7 operates.
The front and rear resin coat films 39 and 39 are each formed by
applying a paint coating including PAI (polyamide imide) and
molybdenum di-sulphide as principal ingredients, on the rear skirt
portion 10 (or the front skirt portion 11), by using a screen
printer, for instance, while implementing, on the skirt portion 10
(or 11), a masking process of using sets of masks identical in
shape to respective vertical grooves 41, 42A, 42B, 43A, and 43B, to
provide on an outer peripheral surface of the skirt portion 10 (or
11), sets of vertical grooves 41, 42A, 42B, 43A, and 43B knurled
with depths within a range of 5 .mu.m or more and 20 .mu.m or less,
or with a depth of 10 .mu.m equal to a thickness of the resin coat
film 39.
Description is now made of friction forces to be developed between
the piston 7 and the wall 6a of the cylinder bore 6.
When reciprocating in the cylinder bore 6, the piston 7 has part of
combustion pressures imposed thereon through an associated
connecting rod 8 (see FIG. 1) and the piston pin 16.
By such combustion pressures, the front and rear skirt portions 11
and 10 are brought into contact with the wall 6a of the cylinder
bore 6, when the left and right piston pin boss portions 15 and 14
have local parts thereof contacting with local parts of the piston
pin 16, which serve as input points of pressing forces acting to
press the skirt portions 11 and 10 against the wall 6a of the
cylinder bore 6.
The piston 7 does reciprocate, undergoing frictional forces
produced between the front and rear skirt portions 11 and 10 and
the wall 6a of the cylinder bore 6, due to reciprocation of the
skirt portions 11 and 10 on the wall 6a of the cylinder bore 6,
under exertion of pressing forces attributable to combustion
pressures.
FIG. 7 illustrates, in an expanded map at the lower half, a
distribution pattern of contact pressures to be produced between
the rear skirt portion 10 (or the front skirt portion 11) and the
wall 6a of the cylinder bore 6. It is noted that, in the map of
FIG. 7, the hatching denotes smaller contact pressures, as it has
shorter intervals.
According to embodiments herein, at the piston 7, the left and
right piston pin boss portions 15 and 14 have local parts thereof
contacting local parts of the piston pin 16, serving as input
points of pressing forces acting to press the front and rear skirt
portions 11 and 10 against the wall 6a of the cylinder bore 6.
Therefore, the rear skirt portion 10 (or the front skirt portion
11) is cooperative with the wall 6a of the cylinder bore 6, to have
increased contact pressures in between, at outer peripheral regions
of the skirt portion 10 (or 11) corresponding to (i.e., overlapping
in a rear view of the piston 7 shown at, e.g., the upper half of
FIG. 7) the left and right piston pin boss portions 15 and 14 or
imaginary extensions thereof.
As shown in FIG. 7, the rear skirt portion 10 (or the front skirt
portion 11) is cooperative with the wall 6a of the cylinder bore 6,
to have contact pressures in between: increased to be larger than
surrounding regions, at local regions (i.e., left and right
columnar regions in the map of FIG. 7) on the outer periphery of
the skirt portion 10 (or 11), corresponding to axially central
parts of the left and right piston pin boss portions 15 and 14; and
increased stepwise to be equal to or larger than the local regions,
at a central zone vehicle-vertically extending including the
circumferential central region 10c (or 11c, see FIG. 5) at the
outer periphery of the skirt portion 10 (or 11), getting maximized
in a vicinity of a length of the central axis C of the piston crown
portion 9 extending downward of the central axis C1 of the piston
pin 16.
According to embodiments herein, as described, the front and rear
skirt portions 11 and 10 are formed in a barrel shape (see FIG. 6)
having circumferential central regions 11c and 10c of the skirt
portions 11 and 10 protruding forward (i.e., constituting apexes)
with respect to a vehicle-longitudinal direction perpendicular to
the central axis C1 of the piston pin 16 in a rear view of the
piston 7. Further, at the front and rear skirt portions 11 and 10,
their outer peripheral surfaces have increased curvatures (see FIG.
5), as they extend from the circumferential central regions 11c and
10c, circumferentially approaching the left and right side wall
portions 13 and 12.
By doing so, at the front and rear skirt portions 11 and 10, the
central skirt parts 37 have most decreased clearances to the wall
6a of the cylinder bore 6, so there can be most increased contact
pressures between the wall 6a o the cylinder bore 6 and the
circumferential central regions 11c and 10c of the skirt portions
11 and 10 with respect to the vehicle-longitudinal direction
perpendicular to the central axis C1 of the piston pin 16 in the
rear view of the piston 7.
Accordingly, at the piston 7, there can be local parts undergoing
decreased clearances between the front and rear skirt portions 11
and 10 and the wall 6a of the cylinder bore 6 and increased contact
pressures between the skirt portions 11 and 10 and the wall 6a of
the cylinder bore 6, requiring conditions for lubrication to be
severer than conditions for lubrication at local parts undergoing
increased clearances between the front and rear skirt portions 11
and 10 and the wall 6a of the cylinder bore 6 and decreased contact
pressures between the skirt portions 11 and 10 and the wall 6a of
the cylinder bore 6.
According to embodiments herein, the piston 7 is adapted for a
preferable lubrication to be performed under such severe conditions
for lubrication. Description will be made of a specific method of
lubricating the piston 7.
It is noted that, at the piston 7, the front and rear skirt
portions 11 and 10 are identical in configuration and performance,
and description is to be made of the rear skirt portion 10.
Further, with respect to moving directions of the piston 7, `ahead
or forward` and `behind or backward` thereof will be referred to
sometimes as `downstream` and `upstream`, respectively.
According to embodiments herein, at the piston 7, the front and
rear skirt portions 11 and 10 each have left and right sets of five
vertical grooves 41, 42A, 42B, 43A, and 43B disposed in a large
clearance region 51 thereof, thereby permitting much oil to be
taken in between the wall 6a of the cylinder bore 6 and large
clearance regions 51 of the skirt portions 11 and 10, when the
piston 7 reciprocates.
As shown in FIG. 12 illustrating a situation at the rear skirt
portion 10, when moving upward, the piston 7 has fluxes of oil
introduced from upstream, to clearances between the upper skirt
part 36 and the wall 6a of the cylinder bore 6.
There can be fluxes of oil introduced to clearances between the
upper skirt part 36 and the wall 6a of the cylinder bore 6, and
partially introduced (as fluxes of oil 01 indicated by broken
lines) to a combination of vertical grooves 42A of an intermediate
length and shortest vertical grooves 43A residing in an upper
combination of left and right sub-regions among upper and lower
combinations of left and right substantially tri-angular
sub-regions (see FIG. 9) of the large clearance region 51,
corresponding in a rear view of the piston 7 to (i.e., overlapping
in FIG. 7) the left and right piston pin boss portions 15 and 14 or
imaginary axial extensions thereof.
There can be fluxes of oil 01 introduced to the upper combination
of left and right vertical grooves 42A and 43A, and further
introduced, passing the upper left and right oblique sides of the
seven-sided shape, to the intermediate clearance region 53, and
still conducted, passing through the upper boundary 37a of the
central skirt part 37, and along the left and right vertical sides
of the seven-sided shape, to go down in the intermediate clearance
region 53.
In other words, there can be fluxes of oil 01 conducted, through
the upper boundary 37a of the central skirt part 37, to a
rectangular oblong-shaped sub-region of the intermediate clearance
region 53 overlapping the central skirt part 37, within a range of
surface region at the outer periphery of the skirt portion 10 that
overlaps extending directions of the left and right piston pin boss
portions 15 and 14. The central skirt part 37 has a maximized
diameter at a central region thereof with respect to an extending
direction of the central axis C of the piston crown portion 9.
The skirt portion 10 has decreased clearances to the wall 6a of the
cylinder bore 6, as it extends from the left part 10a or the right
part 10b toward the circumferential central region 10c. Hence,
there can be fluxes of oil (as oil 02 indicated by broken lines)
introduced through the upper left or right innermost vertical
groove 43A or 43A, or from over a sub-region of the large clearance
region 51 residing still inside of the innermost vertical grooves
43A and 43A, and passing the upper left or right oblique side of
the seven-sided shape, to the intermediate clearance region 53, and
conducted toward the circumferential central region 10c of the
skirt portion 10, to introduce to the small clearance region
52.
By doing so, at the skirt portion 10, there can be favorable
lubrication implemented over a combination of the small clearance
region 52 and the intermediate clearance region 53, as well as over
associated regions on the wall 6a of the cylinder bore 6.
It is noted that there can be ample oil between the large clearance
region 51 of the skirt portion 10 and the wall 6a of the cylinder
bore 6, allowing for resistances to be generated by such oil, as
necessary.
According to embodiments herein, there can be fluxes of oil 01
introduced to the large clearance region 51 of the skirt portion
10, and separated to conduct from any one of upstream vertical
grooves (i.e., the upper left and right vertical grooves) 42A and
43A to an associated one of downstream grooves (i.e., the lower
left and right vertical grooves) 42B and 43B, or directly from a
region vicinal to the top side to a region vicinal to the bottom
side of the four-sided shape by one of the outermost left and right
longest vertical grooves 41. By doing so, there can be fluxes of
excessive oil discharged downstream of the vertical groove 41, 42B,
or 43B, smoothly and without stagnation, thus allowing for dragging
resistances by oil to the piston 7 to be reduced.
On the other hand, as shown in FIG. 13 illustrating a situation at
the rear skirt portion 10, when moving downward, the piston 7 has
fluxes of oil introduced from upstream, to clearances between the
lower skirt part 38 and the wall 6a of the cylinder bore 6.
There can be fluxes of oil introduced to clearances between the
lower skirt part 38 and the wall 6a of the cylinder bore 6, and
partially introduced (as oil O3 indicated by broken lines) to a
combination of vertical grooves 42B of an intermediate length and
shortest vertical grooves 43B residing in an lower combination of
left and right tri-angular sub-regions of the large clearance
region 51, overlapping extending directions of the left and right
piston pin boss portions 15 and 14.
There can be fluxes of oil O3 introduced to the lower combination
of left and right vertical grooves 42B and 43B, and further
introduced, passing the lower left and right oblique sides of the
seven-sided shape, to the intermediate clearance region 53, and
still conducted, passing through the lower boundary 37b of the
central skirt part 37, and along the left and right vertical sides
of the seven-sided shape, to go up in the intermediate clearance
region 53.
In other words, there can be fluxes of oil O3 conducted, through
the lower boundary 37b of the central skirt part 37, to the
rectangular oblong-shaped sub-region of the intermediate clearance
region 53, within the range of surface region at the outer
periphery of the skirt portion 10 overlapping extending directions
of the left and right piston pin boss portions 15 and 14.
There can be fluxes of oil (as oil 04 indicated by broken lines)
introduced through the lower left or right innermost vertical
groove 43B or 43B, or from over a sub-region of the large clearance
region 51 residing still inside of the innermost vertical grooves
43B and 43B, and passing the lower left or right oblique side of
the seven-sided shape, to the intermediate clearance region 53, and
conducted toward the circumferential central region 10c of the
skirt portion 10, to introduce to the small clearance region
52.
By doing so, at the skirt portion 10, there can be favorable
lubrication implemented over a combination of the small clearance
region 52 and the intermediate clearance region 53, as well as over
associated regions on the wall 6a of the cylinder bore 6.
Further, there can be fluxes of oil O3 introduced to the large
clearance region 51 of the skirt portion 10, and separated to
conduct from any one of upstream vertical grooves (i.e., the lower
left and right vertical grooves) 42B and 43B to an associated one
of downstream grooves (i.e., the upper left and right vertical
grooves) 42A and 43A, or directly from a region vicinal to the
bottom side to a region vicinal to the top side of the four-sided
shape by one of the outermost left and right longest vertical
grooves 41. By doing so, there can be fluxes of excessive oil
discharged downstream of the vertical groove 41, 42B, or 43B,
smoothly and without stagnation, thus allowing for dragging
resistances by oil to the piston 7 to be reduced.
In particular, according to embodiments herein, the piston 7 has
the left and right vertical grooves 41 continuously extending from
the upper skirt part 36 to the lower skirt part 38, at regions
involving largest clearances between the skirt portion 10 and the
wall 6a of the cylinder bore 6, among regions in the large
clearance region 51.
By doing so, the piston 7 in the course of reciprocation is adapted
(when handling fluxes of oil as introduced to clearances at regions
involving largest clearances between the skirt portion 10 and the
wall 6a of the cylinder bore 6, among regions in the large
clearance region 51), to use the vertical grooves 41 for
discharging such oil to downstream ends, thus affording to
discharge the more oil to downstream ends.
On the other hands, the piston 7 is cooperative with the wall 6 of
the cylinder bore 6 to introduce in between a flow of oil
proportional to a speed of the piston 7. Therefore, in a low
rotation speed range of the engine 1, such the flow of oil is
decreased, with anxieties about deteriorated lubrication between
the wall 6 of the cylinder bore 6 and the small clearance region 52
and the intermediate clearance region 53.
Further, in a high rotation speed range of the engine 1, the piston
7 has an increased flow of oil introduced between the large
clearance region 51 and the wall 6 of the cylinder bore 6, giving
rise to an increased drag resistance to the piston 7 by oil.
According to embodiments herein, the piston 7 is adapted in the low
rotation speed range of the engine 1, to have a sufficient flow of
oil introduced from the vertical grooves 42A, 42B, 43A, and 43B, to
clearances between the wall 6 of the cylinder bore 6 and the small
clearance region 52 and the intermediate clearance region 53,
allowing for an enhanced lubrication between the wall 6 of the
cylinder bore 6 and the small clearance region 52 and the
intermediate clearance region 53.
Further, the piston 7 is adapted in the high rotation speed range
of the engine 1, to have a flow of oil introduced to clearances
between the large clearance region 51 and the wall 6 of the
cylinder bore 6, and discharged through the vertical grooves 41,
42A, 42B, 43A, and 43B, to downstream ends, smoothly and without
stagnation, allowing for a reduced drag resistance to the piston 7
by oil. Such being the case, the piston 7 is adapted to make
lubrication to the skirt portion 10 compatible with reduction of
drag resistance to the piston 7, irrespective of the rotation speed
of the engine 1 to be increased or decreased.
FIG. 14 is a data on experiments including measuring frictional
forces between a wall of a cylinder bore and skirt portions using
resin coat films in the past having no vertical grooves formed
therein or those using resin coat films 39 involving vertical
grooves 41 and the lie formed therein according to embodiments
herein.
This experimental data involves results of varying the rotation
speed of an engine for operating a piston, using a device for
evaluation of frictional forces acting on the piston proper. There
was a result on a piston 7 using resin coat film layers 39
according to embodiments herein, including data on frictional
forces between a wall of a cylinder bore and skirt portions,
ensuring a reduction of approximately 10% in average in comparison
with a piston using resin coat film layers in the past.
Such being the case, according to embodiments herein, a resin coat
film 39 formed on a skirt portion 10 of a piston 7 has a four-sided
outer peripheral region knurled at upper and lower regions thereof
corresponding in a rear view of the piston 7 to an upper skirt part
36 and a lower skirt part 38 of the skirt portion 10 extending in
parallel with an axial direction of left and right piston pin boss
portions 15 and 14, with a combination of short vertical grooves
43A and 43B and medium-length vertical grooves 42A and 42B
extending in parallel with a central axis C of a piston crow
portion 9, and at left and right edge regions thereof, with long
vertical grooves 41.
In other words, the rear skirt portion 10 composed of the upper
skirt part 36, the central skirt part 37, and the lower skirt part
38 (thus involving at least the upper skirt part 36 and the lower
skirt part 38) has the resin coat film 39 formed on an peripheral
surface thereof, and knurled at a four-sided outer peripheral
region thereof with two sets of five vertical grooves 41, 42A, 42B,
43, and 43B extending in parallel with the central axis C of the
piston crown portion 9. Those vertical grooves 41, 42A, 42B, 43,
and 43B are located within ranges in extending directions of the
left and right piston pin boss portions 15 and 14, (that is,
overlapping them 15 and 14) when viewed from behind in a
vehicle-longitudinal direction perpendicular to the central axis C
of the piston crown portion 9.
By doing so, during reciprocation of the piston 7, there can be
fluxes of oil introduced between the wall 6a of the cylinder bore 6
and a central region on the peripheral surface of the skirt portion
10 that undergoes small clearances and high contact pressures, when
contacting an associated region on the wall 6a of the cylinder bore
6. This situation permits lubrication between the skirt portion 10
and the wall 6a of the cylinder bore 6 to be enhanced, allowing for
a prevented seizing between the skirt portion 10 and the wall 6a of
the cylinder bore 6.
Further, according to embodiments herein, at the piston 7, there
can be an ample flux of oil introduced between the large clearance
region 51 of the skirt portion 10 and the wall 6a of the cylinder
bore 6, and discharged downstream of movement of the piston 7 by
vertical grooves 41, 42A, 42B, 43, and 43B, smoothly without
stagnation. By doing so, dragging resistances by oil to the piston
7 can be reduced, affording to prevent fuel economy of the engine 1
from getting worse.
Further, according to embodiments herein, at the piston 7, the
skirt portion 10 is configured to have increased curvatures, as it
circumferentially extends from the circumferential central region
10c toward the left and right side wall portions 13 and 12.
Accordingly, the skirt portion 10 has decreased clearances to the
wall 6a of the cylinder bore 6, as it extends either of the left
side part 10a and the right side part 10b of the skirt portion 10
toward the circumferential central region 10c.
And, the sets of five vertical grooves are each disposed to have
the vertical groove 41, the vertical groove 42A or 42B, and the
vertical groove 43A or 43B mutually neighboring in a
circumferential direction of the skirt portion 10. The vertical
groove 41 disposed nearer to the side wall portion 12 or 13 is
knurled with a greater length than the vertical grooves 43A and 43B
disposed nearer to the circumferential central region 10c of the
skirt portion 10 in an extending direction of the central axis C of
the piston crown portion 9.
By doing so, three can be fluxes of oil smoothly introduced to the
large clearance region 51 on the resin coat film 39 of the skirt
portion 10, affording to employ the left and right long vertical
grooves 41 and 41 to have fluxes of excessive oil, unused for
lubrication, smoothly discharged downstream of the piston 7,
without stagnation. Hence, dragging resistances by oil to the
piston 7 can be the more effectively reduced.
Further, according to embodiments herein, at each vertical groove
set of the piston 7, the upper vertical grooves 42A and 43A set
shorter than the vertical groove 41 are disposed to extend between
the upper edge 39a (see FIG. 8) of the resin coat film 39 on the
skirt portion 10 and a local region just above the upper boundary
37a that is a boundary of the central skirt part 37 defining the
upper skirt part 36.
Further, at each vertical groove set of the piston 7, the lower
vertical grooves 42B and 43B set shorter than the vertical groove
41 are disposed to extend between the lower edge 39b (see FIG. 8)
of the resin coat film 39 on the skirt portion 10 and a local
region just below the lower boundary 37b that is a boundary of the
central skirt part 37 defining the lower skirt part 38.
By doing so, there can be minute variations in clearance between
the wall 6a of the cylinder bore 6 and the skirt portion 10 of the
piston 7, so there can be fluxes of oil effectively introduced from
the vertical grooves 43A and 43B to vicinities of the upper
boundary 37a and the lower boundary 37b of the central skirt part
37 undergoing increased contact pressures between the wall 6a of
the cylinder bore 6 and the skirt portion 10.
Accordingly, there can be fluxes of oil effectively introduced
between the wall 6a of the cylinder bore 6 and the central skirt
part 37, allowing for effective lubrication to the wall 6a of the
cylinder bore 6 and the central skirt part 37.
Further, according to embodiments herein, at the piston 7, the
vertical grooves 41, 42A, 42B, 43A, and 43B are knurled with a
depth of 10 .mu.m allowing for smooth communication of oil to the
vertical grooves 41, 42A, 42B, 43A, and 43B. The vertical grooves
41, 42A, 42B, 43A, and 43B may well have depths thereof within a
range of 10 .mu.m or more and 20 .mu.m or less.
At the vertical grooves 41, 42A, 42B, 43A, and 43B, if given a
depth of 5 .mu.m or less, the vertical grooves 41, 42A, 42B, 43A,
and 43B may constitute a difficulty for oil to be conducted, and
may be unfavorable. Or, if given a depth of 20 .mu.m or more, the
vertical grooves 41, 42A, 42B, 43A, and 43B may cause the resin
coat film 38 to have an increased thickness, leading to stagnation
of excessive oil, and may be unfavorable.
While embodiments of this invention have been described, it is
apparent that some artisan could have made changes without
departing from the scope of this invention. It is intended that any
and all such modifications and equivalents are involved in the
appended claims.
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